US3230938A

US3230938A - Rotary internal combustion engine

Info

Publication number: US3230938A
Application number: US315029A
Authority: US
Inventors: Edward J Hojnowski
Original assignee: Individual
Current assignee: Individual
Priority date: 1963-10-09
Filing date: 1963-10-09
Publication date: 1966-01-25
Anticipated expiration: 1983-01-25

Description

Jan- 25, 1966 E. J. HoJNowsKl ROTARY INTERNAL COMBUSTION ENGINE 3 Sheets-Sheet 1 Filed 0G12. 9, 1963 Jan- 25, 1966 E. .1. HoJNowsKl 3,230,938

ROTARY INTERNAL COMBUSTION ENGINE Filed Oct. 9, 1963 5 Sheets-Sheet 2 Jan. 25, '1966 E. J. HoJNowsKl 3,230,938

ROTARY NTERNAL COMBUSTION ENGINE Filed Oct. 9, 19615 3 Sheets-Sheet 3 United States Patent O `3,230,938 RTARY INTERNAL .COMBUSTEON ENGINE Edward J. Heinen/ski, 272 Broad St., New Britain, Conn. Fiied Get. 9,1933, Ser. No. B-,G29 11 Claims. (Cl. 12S-16) This invention -r-elates to internal combustion engines and more particularly to an engine in which a rotating member is driven by a succession of explosive impulses contained in peripherally spaced chambers defined in part by said rotating-member. t

A general object of the presen-t invention is to provide a rotary engine vhaving -a minimuml 'of moving parts so that the initial cost of Isuch an engine, as well as the maintenance expenses thereof, can be held to very low values.

Another general object of the present invention is to provide a rotary engine .in which a plurality of peripherally spaced expansion chambers are filled with an air charge by one or more novel compression chambers.

Still another object of the present invention is to provide a rotary engine which is peculiarly well suited to that system of carburetion known as fuel injection.

A still further object ofthe present invention is to provide a rotary engine which avoids the use of eccentrically mounted shafts or the like, and therefore avoids the extensive balancing usually associated 4with rotary engine designs.

Yet another object of the present invention is to provide a rotary engine in which the exhaust gases are ejected from a rotating part of the engine so that the back pressure :felt by the engine is lower than the ambient pressure of the atmosphere in which the engine is operating.

A more speci-lic object of the present invention is to provide a rotary engine in which a series of reciprocating elements cooperate with said rotating member to define .the peripherally spaced expansion chambers, which elements simultaneously operate on the air charge in said compression chambers to compress the same. I

The drawings show preferred embodiments of the inveniton and such embodiments will be described, but it will be understood that various changes may be made from the constructions disclosed, and that the drawings and description are not to be construed as defining or limitingthe scope of the invention, the claims forming a part of this specification being relied upon for that purpose.

Of the draw-ings:

FG. 1 is a plan view of a preferred embodiment of the present invention, the lower half of the engine being shown in section to better illustrate 4internal parts;

FIG. 2 is a sectional view of the FIG. 1 engine along the line -2-2 of that iigure;

FliG. 3 -is a sectional view of the FIG. 1 engine along the line 3-3 of that ligure;

FIG. 4 is an alternative construction for the expansion joint used to connect the front and rear portions of the rotor;

FIG. 5 is a plan view of a sliding abutment of the FIG. 1 engine;

FIG. 6 is a sectional view of the FIG. 5 abutment along the line 6 6 of that figure;

FIG. 7 is a schematic view of the FIG. 1 engine at a particular instant of time; and

FIG. 8 is a schematic vieW similar to FIG. 6 but at a slightly later instant of time.

Referring now to FIGS. l and 2, a rotary engine of the present invention is shown as comprising an outer rotor 12 supported for rotation about a central axis 14 by an annular stator 16. An inner shaft 18 rotates about the same axis inside the stator and is generally hollow as best shown in the lower half of FIG. 1.

In the preferred embodiment shown, an engine drive, or output, shaft 2G is provided at the lfront of the engine "ice and is rigidly connected to the hollow shaft 18 by a sun gear 2-2. The sun gear has a peripheral iiang'e 24 which is screwed to a front portion 2o of the hollow shaft 1S by a plurality of circumaxially spaced screws 2S, 28 and a hub portion 39 which may be keyed to the drive shaft 2t) as shown in FIGS. 2 and 3.

The upper half of FIG. 1 shows the sun gear 22 in engagement with a set of three planet gears 32, 32 (one shown) which in turn engage a ring gear 34 for rotation of the latter in a direction opposite to said sun gear 22. The

planet gears

32, 32 are rotatably supported inthe fixed framework of the stator 16 by three bolts 36, 3'6 received in the

holes

38, 38. The ring gear 34 is provided with an annular flange 4t) which is screwed to the front portion 42 of the rotor 12 by a plurality of circumaxially spaced

screws

43, 43. As so arranged, clockwise rotation 'of the rotor in the direction of .the arrow 44 results in counterclockwise rotation of the hollow shaft 1-8, as indicated by the arrow '46. The three planet gears 32, 32 'are further supported in the fixed framework of the machine by a stationary spider having three

legs

49, 49 for the

gears

32, 32. This spider serves to rotatably support the drive shaft 20, the inner ends of each of said spider legs 419, 49 defining a hub 50 which rotatably supports said shaft as best shown in FIG. 3. The spider also functions as a means for mounting the entire engine. Three

holes

52, 52 are provided for .that purpose in each of the generally triangular o-uter end portions S4, 54 of said

spider legs

49, 49.

Turning now to the construction of the outer rotor 12 in greater detail, a rear portion 5'6 is bolted to the front por- .t-ion 42 thereof by a plurality of peripherally arranged bolts S8, 53. The rear portion 56 denes an axially ex'- tending internal surface 64) which varies radially around the rotor 12. 'Ilwo diametrically opposed

sections

62, 62 of said internal surface are approximately the same di'- arneter as the outer diameter of the annular stator 16. As shown two circumaxially spaced

sections

64, 64 of said internal surface between these sections '62, 64 are recessed radially outwardly with respect to the central axis 14 to dene two outer cavities 65 and 68 best shown in the lower hal-f of FIG. 1. These outer cavitiesv o6 and 68 are sealed from the outside atmosphere except for two

exhaust ports

70 and 72 defined by the trailing sections of each of said cavities.

Asbest shown in FIG. 2, the annular stator 16 is of onepiece construction and the front and rear rotor portions 42 and `Se respectively, are slidably received on outer front and rear flanges 74 and 75 respectively, defined by said stator. The outer cavities serve to define in part the expansion chambers of the engine in a manner to be described in greater detail hereinbelow and hence require means for accommodating the thermal expansion of the rot-or '12. More specifically, the different rates of thermal expansion experienced by the rotor and the stator are accommodated by a novel construction for joining the front and rear portions of the former. As shown, a generally :peripherally extending groove 718 is provided on the inside surface of the front portion 42, and an axially extend-ing part of said rear portion 56 is slida'bly received in this groove 78. These `front and rear rotor po-r- .

tions

42 and 56 respectively are bolted together by the above-mentioned axially extending .

bolts

58, 58 which are received in aligned holes S2', 82 provided therefor in radially extending ears 84, '8o on said front and rear rotor portions. A compression spring e8 is provided between the rear face of each ear 816, and a nu-t 96 on each bolt, so as to permit the axially extending part Si) of the rotor rear portion to slide axially in the groove 7S of the rotor front portion. As so constructed, the rotor 12 will be seen to be relatively unaffected by any differential rate of thermal expansion or contraction with respect to the stator lo.

"A ED FIG. 4 illustrates an alternative construction for accommodating the thermal expansion of the rotor 12. The construction there shown is generally similar to that just described with reference to FIG. 2 except for the addition of hydraulic damping means 92 concentrically arranged within a helical spring 88a. The damping means 92 is seen to comprise a sealed cylinder S14-having a hollow interior bore 96 through which a lbolt 58a extends carrying a piston 98. The latter has a small opening 99 generally axially thereof through which uid in the cylinder must pass as the piston traverses the bore 96 due to lthermal expansion or contraction of the rotor 12. with respect to the stator (not shown).

Turning now to the construction of the hollow shaft 18, FIG. 2 reveals that said shaft is constructed in a -manner generally similar to that 'of the rotor 12, a rear portion 180 being bolted to the front portion 26 'of the Shaft by a plurality of peripherally arranged

bolts

126, 126. The rear portion i) has an axially extending external surface .104 which varies radially around the shaft 18. A diametrically opposed portion 106 of said internal surface is of approximately lthe -same diameter as the inner diameter of the annular stator 16. As shown in FIG. l, the remaining portion of said external surface 104 is recessed radially inwardly with respect to the central axis 14 to dene an inner cavity 108. This inner cavity is sealed from the outside atmosphere except for an intake port 110 defined thereby and best shown in FIGS. 3, 7 and 8.

As mentioned, the annular stator is of one-piece construction and the front and rear shaft portions, 26 and 100, respectively, are slidably received on front and rear circular anges, 112 and 114 respectively, defined by said stator. The stator serves to define in part the expansion chambers of the engine in a manner to be described in greater detail hereinbelow and hence means are provided for accommodating the thermal expansion of the stator with respect to the shaft 18. As shown, ysaid means are generally similar to that employed with refe-rence to the two-piece rotor described hereinabove. A generally peripherally extending groove l116 is provided on the inside surface of the front portion 26, and an axially extending part 118 of said rear portion 180 is slidably received therein. The

axially extending bolts

126, 126 join these .front and

rear shaft portions

26 and 100 respectively, and a compression spring 122. is provided between the rearface of an ear 124 on the rear shaft portion and a nut 120 on each of said

bolts

126, 126 so as to permit the axially extending part 118 of the rear shaft portion 100 to slide in the groove 116 of the front shaft portion `26. As so constructed, the shaft 18 is relatively unaffected by any differential rate of thermal expansion or contraction with respect to the stator 16.

It w-ill -be apparent that the hydraulic damping means of FIG. 4 could be employed in addition to the

springs

122, 122 and the remarks made in connection with the description of that figure apply equally to the thermal expansion or contraction of the stator with respect to the shaft 18.

As mentioned, the stator 16 is annular in planform having cylindrical outer and inner surfaces which define in part said outer and inner cavities respectively. Also part of said ystator are the outer and inner pairs of circular lianges 74, '76 and 112, 114 respectively, which rotatably support the rotor and shaft respectively. With further reference to the one-piece stator 16, a series of three generally radially extending

slots

128, 128 are defined therein at circumaxially equally spaced locations. These

slots

128, 128 slidably receive three vane-'like abutments 130, 13@ to be described in greater detail hereinbelow. From FIG. 7 it will be apparent that the angular spacing between these slots, and their associated abutments determines the circumferential extent of the

outer cavities

66 and 68 and that this last-mentioned dimension, in conjunction with the relative rotational speeds of the rotor 12vand the shaft 18, determines the circumferential extent of the inner cavity 188. As shown, these outer cavities, 66 and 68,'v have symmetrically arranged intermediate sections of constant radial width, and also antisymmetrically arranged leading and trailing end sections the radial width of which varie-s from a minimum adjacent the outer annular -surface of the stator to a maximum at said intermediate sections.4 The hollow shaft 18, which is caused to rotate at twice the rotational speed of said rotor and in the opposite direction, is recessed radially inwardly as mentioned and the shape of this Vrecessed portion is such that a constant radial differenceis maintained between the innerand outer cavity surfaces at these

slots

128, 128. As so constructed and arranged, the abutments i139, will be seen to maintain contact with these inner and outer cavity surfaces when the rotor and shaft rotate in the directions indicated in FIGS. 7 and 8.

Finally, still with reference to the stator16, except for the

slot defining portions

128, 128 thereof, and the

hole defining portions

38, 38 adjacent thereto, the stator 16 is substantially hollow having vthree circumaxially spaced

openings

132, 132 therethrough. These openings provide access to a series of three spark plugs 134, 134 and a series of three

fuel injection nozzles

136, 136 associated with each of said

slots

128, 128.

Turning now to the con-struction of the sliding

abutments

130, 130, FIGS. 5 and 6 show the construction of one of these. Each abutment carries inner and. outer sealing means, indicated generally at 138 and 141, respectively and located at each radial end thereof. As shown, said sealing means comprise inner and outer

cylindrical members

140, 140, which are rotatably supported in inner and

outer arms

142 and 144 respectively. In the construction shown, arm 142 and arm 144V are reciprocably received in inner and outer slots, 146 and 148, respectively, provided therefor in the inner and outer ends of a generally rectangular abutment base 159. Also included in each abutment 130 are `biasing means lfor urging the inner and outer sealing means away from the base 150. As shown, said biasing means comprise a pair of compression springs 152, 152 carried in cylindrical bores 154, 154 provided therefor in the center portion of the base. A pair of

cylindrical posts

156, 156 are provided on each

arm

142 and 144 and are slidably received in said bores 154, 154 to prevent any axial displacement of the inner and outer sealing means, 138 land 141 respectively, with respect to the generally radially reciprocable base 150.` Y

With further reference to the abutment base 150, two axially spaced radially extending flanges A157, 157 are provided at the sides thereof to define an abutment of substantially the same thickness yas the corresponding dimension of the slot 128. From FIG'. 1 it will be apparent that these

flanges

157, 157 do not interfere with the reciprocable feature of the inner and outer sealing means, 138 and 141 respectively, the ends of said ilange-s being so shaped as to accommodate-the -

respective arms

142 and 144 thereof.

Referring now to FIGS. 7 and 8, the operation of the above-described engine can be conveniently demonstrated. It will be apprecated that air can be drawn into the hollow shaft 18 by suitable air inductionmeans (not shown), and that cooperating means can be providedv for metering fuel into the spaces between the abutments and the slot defining portions of the stator 16. Both the above means may be conveniently referred to as carburetor means for combining fuel with the air, and except for the location of the

fuel injection nozzles

136, 136, need not be described in detail here since the presenty invention relates primarily to a novel internal combustion engine and not to the means for feeding the air charge into said engine.

The air intake port 11@ provides a path for the air from the hollow interior of the shaft 18 into the inner cavity 188. As this shaft rotates in the direct-ion ofthe arrow 46, the adjacent abutment 130 will be seen to define a compression chamber A, which chamber rotates with the shaft and varies in volume as indica-ted by the characters A1, A2, A3 and A4 seen alternately in FIGS. 7 and 8. It will be apparent that the rotating intake port 110 willcapture a large volume of air as a result of its rotation since the leading andt-railing edges, 109 and `111 respectively, lare located at different radii from the axis lof rotation 14. yIt will also be apparent that the volume of the compressi-on chamber A is considerably less at A4 than at A3 resul-ting in the compression of the air charge therein as the shaft rotates in the directi-on indica-ted.

Referring .now t-o FIG. 8, a combustion chamber, indicated generally at B; is defined in the linner and outer cavities; 108 and 66 respectively, by the .abutment 130 and the slot defining portion of the stator 16. It will be observed 'that' the Compressed .air charge A4 will be moved into this combusti-on chamber as the contrarotating shaft and rotor reach the position indicated at B. As best shown in lFIG. 1, the fuel injection nozzle 136 and

spark plug

1,34 cooperate to cause an explosion in this chamber. The resulting expansion caused by the heat of combustion imparts a successive series of explosive impulses to the leading end sections of each of the

outer cavities

66 and 68 driving the rotor 12 in the d-irection indicated.

An expansion chamber C is defined in each of the outer cavities 66 .and 68 by the sliding abutment 130 which traverses said cavity as the rot-or rotates. This chamber C accommodates the expanding ygases due to combustion in a controlled manner whereby the energy of combustion can be conveniently converted into usable kinetic energy. The characters C1, C2 and C3 depict the variation in volume of this chamber and the latter, C3, also represents the beginning of the exhaust porti-on of the cycle described herein.

The

exhaust ports

70 and 72 will be seen to occupy a very .advantageous location on the rotary engine shown in that the rotor 12, which defines these ports, -is continually rotating in the direction indicated and a region of relatively low pressure is created in the area of said exhaust ports. As so constructed, the back pressure against which the engine is working is lower than the ambient pressure of the atmosphere in which the engine is operating.

Another yadvantage to the exhaust port location shown is that very little :cooling is required for the engine in normal operating conditions. Where elevated temperatures are .apt to be encountered during engine operation cooling fins could be easily `provided at the periphery of the rotor to conduct away excess heat from the expansion chambers defined therein. Since the rotor will receive most of the heat of combusti-on due to the burning gases and since the rotor has its entire external surface exposed to the atmosphere the rotary engine sh-own has obvious advantages in any environment.

In conclusion, the rotary internal combusti-on engine shown has all of the usual advantages of .rotary engine designs generally, including that of permitting a degree of compression of the air charge prior to combustion, which compression is independent of the degree of expansion required in absorbing the energy of the burning fuel and .air mixture. In terms of engine efficiency it is well known that the compression ratio and the expansion ratio are determinative of the thermal efficiency of an internal combustion engine whether of the rotary or conventional piston type. One .advantage of the former o-ver the latter is that its construction permits the expansion ratio to be greater than the compression ratio. Since the compression ratio is inherently limited as a result of the fuel used in any internal combustion engine, Iit follows that the rotary engine is inherently more eicient because the expansion ratio is independent of the compression ratio.

The present invention not only -permits a large expansion ratio but does so without the lbulky size normally associated with a rotary engine. It will be apparent that the expansion ratio is directly relatedl to the size :of the expansion chamber. Most rotary engine designs achieve a high expansion ratio by providing for a relatively large cavity in the rotating member. In the engine shown for example, the expansion ratio could be materially -increased by increasing the diameter `of the rotor. However, it should be noted that this approach would require a stator of increased size creating balancing problems as well vas larger and heavier bearings and the like. The present design seeks to optimize the volume of the outer cavities, 66 and 68, without incurring any .size or weight penalty by inclining the abutments 130, with respect to the radial direction Ias best shown in FIGS. 7 Iand 8. As so lconstructed and arranged, the effective expansion ratio is materially increased over that possible with purely 4radially reciprocable abutments. As noted this increase results in avery efficient rotary engine without the bulky size rnormally .associated with rotating engines generally.

The invention claimed is:

1. An internal combustion engine comprising an annular stator, a concentric hollow shaft contacting the inner cylindrical surface of said stator and having at least one portion of its periphery recessed radially inwardly to define an inner cavity, means `for introducing air into said inner cavity, a rotor concentric with said stator and contacting the outer cylindrical surface thereof, said rotor having at least two circumaxially spaced portions of its internal surface recessed radially loutwardly to define two outer cavities, exhaust ports communicating with each of said outer cavities, means for rotatively connecting said shaft to said rotor whereby the former ldrives the latter in an opposite direction with respect thereto, at least three generally radially extending abutments slidably received in circumaxially spaced slots provided therefor in said stator, each of said abutments traversing said inner cavity as the shaft rotates to define a compression chamber therein, each of said abutments traversing said outer cavities as lthe rotor rotates to define expansion chambers therein, each of said abutments together with the adjacent slot defining porti-on of said stator defining an air passageway whereby a part of said inner cavity is caused to successively communicate with a part of each of said outer cavities for the supply o-f compressed air to the latter, and fuel introducing and igniting means for said outer cavities.

2. An internal combustion engine `as defined in claim l wherein said air induction means includes an intake port defined by said hollow shaft and adapted to rotate therewith, said intake port having leading and trailing edge porti-ons which are at different radial distances from the axis of rotation of said shaft whereby a greater quantity of the air in said hollow .shaft can pass outwardly through said intake port than would be the case if both of said edges were yat the same radial distance from said axis.

3. An internal combustion engine las defined in claim .1 wherein eac-h of said exhaust ports are defined by said rotor and adapted to rotate therewith, each of said exhaust ports being s-o located with respect to the periphery of said rotor that the spent gases of combustion are exhausted into a region `of lower back pressure than that of the .ambient atmosphere in which the engine is operating.

4. An internal combustion engine as defined in claim 1 wherein the ratio of :the angular speeds of said shaft and said rotor is a whole integer, and wherein both of said .angular speeds lare measured relative to said stator.

5. An internal c-ombust-ion engine as defined in claim 4 wherein said means for .so rotating said rotor and shaft comprise a sun gear attached to the shaft, a ring gear attached to the rotor, .and at least one planet gear r-otatably supported by the .stator so as to engage both of these.

6. An internal combustion engine as defined Ain claim 4 wherein the recessed portion of said shaft and the recessed portions of said rotor are so shaped that the radial dierence between these surfaces at the circumaxially spaced slots in sai-d stator is a constant.

7. An internal combustion engine as defined in lclaim 6 and including means for yaccommodating the differential rate of thermal expansion and contraction of the rotor with respect to the stator.

8. An internal combustion engine as dened in claim 6 wherein each of said abutments has an inner end which engages the periphery 4of said shaft, and an ou-ter end which engages the internal surface of said rotor whereby said abutments are caused to reciprocate in said stator slots as said shaft and rotor rotate.

9. An internal combustion engine -as defined in claim 8 vand inclu-ding sealing Imeans carried yby each abutment at the inner and `outer ends thereof, and biasing means included in leach :of said abntrnen-ts for urging said inner and -outer sealing means radially inwardly 'and radially outwardly respectively, whereat said inner .sealing means is caused to engage vsaid shaft periphery .and said outer sealing means to engage said rotor intern-al surface.

10. An internal combustion engine as defined in claim 9 wherein sai-d abutments are inclined with respect to the radial direc-tion whereby toin-crease the volume of the expansion chambers in said outer cavities.

11. An :internal combustion engine as defined in claim 10, wherein said fuel'introducing means comprises a plurality of fuel injection nozzles which are spported Iadjant to each of .the slot defining portions of said sta-tor so as to inject fuelv directly into said passageway whereby the vaporizing of said fuel is facilitated by reason of the lair passing therethrough.

References Cited by the Examiner DONLEY I. STOCKING, Primary Exaniner. KARL J. ALBRECHT, Examiner.

Claims

1. AN INTERNAL COMBUSTION ENGINE COMPRISING AN ANNULAR STATOR, A CONCENTRIC HOLLOW SHAFT CONTACTING THE INNER CYLINDRICAL SURFACE OF SAID STATOR AND HAVING AT LEAST ONE PORTION OF ITS PERIPHERY RECESSED RADIALLY INWARDLY TO DEFINE AN INNER CAVITY, MEANS FOR INTRODUCING AIR INTO SAID INNER CAVITY, A ROTOR CONCENTRIC WITH SAID STATOR AND CONTACTING THE OUTER CYLINDRICAL SURFACE THEREOF, SAID ROTOR HAVING AT LEAST TWO CIRCUMAXIALLY SPACED PORTIONS OF ITS INTERNAL SURFACE RECESSED RADIALLY OUTWARDLY TO DEFINE TWO OUTER CAVITIES, EXHAUST PORTS COMMUNICATING WITH EACH OF SAID OUTER CAVITIES, MEANS FOR ROTATIVELY CONNECTING SAID SHAFT TO SAID ROTOR WHEREBY THE FORMER DRIVES THE LATTER IN AN OPPOSITE DIRECTION WITH RESPECT THERETO, AT LEAST THREE GENERALLY RADIALLY EXTENDING ABUTMENTS SLIDABLY RECEIVED IN CIRCUMAXIALLY SPACED SLOTS PROVIDED THEREFOR IN SAID STATOR, EACH OF SAID ABUTMENTS TRAVERSING SAID INNER CAVITY AS THE SHAFT ROTATES TO DEFINE A COMPRESSION CHAMBER THEREIN, EACH OF SAID ABUTMENTS TRAVERSING SAID OUTER CAVITIES AS THE ROTOR ROTATES TO DEFINE EXPANSION CHAMBERS THEREIN, EACH OF SAID ABUTMENTS TOGETHER WITH THE ADJACENT SLOT DEFINING PORTION OF SAID STATOR DEFINING AN AIR PASSAGEWAY WHEREBY A PART OF SAID INNER CAVITY IS CAUSED TO SUCCESSIVELY COMMUNICATE WITH A PART OF EACH OF SAID OUTER CAVITIES FOR THE SUPPLY OF COMPRESSED AIR TO THE LATTER, AND FUEL INTRODUCING AND IGNITING MEANS FOR SAID OUTER CAVITIES.